Gas turbine fuel control having both a normal speed and an emergency control



May 13, 1952 w. KEiL 2,596,315 GAS TURBINE FUEL CONTROL HAVING BOTH A NORMAL SPEED'AND AN EMERGENCY CONTROL Filed April 29, 1949 lfeil IN VEN TOR.

Patented May 13, 1952 UNITED STATES PATENT OFFICE 2,596,815 GAS TURBINE FUEL CONTROL HAVING BOTH A NORMAL SPEED AN D" AN EMERGENCY CONTROL Leonard W. Keil, Wayne, Mich, assignor to George M. Holley and Earl Holley Application April 29, 1949, Serial No. 90,444

' 12 Claims. (01. 6039.28)

(1)) During acceleration, and until governing,

commences, the normal pump should not be interfered with and another object is to prevent the emergency control from being brought into action-until acceleration, is completed and governing commences.

Another object is to provide a speed limiting device to limit the speed of the gas turbine, that is; the speed possible'with the manual control being unlimited some safety device is neces sary. 1

((1) To arrangeto automatically dump the fuel in the inlet manifold at. the time the turbine stops. f

(e) To arrange means whereby both the manual and normal controls of the fuel available for acceleration is decreased as the altitude increases, andincreases slightly with speed and decreases slightly with temperature.

(1) Another object is to hold the control in the manual .position after once going into manual control, otherwise hunting would occurand the 1 same means would enable the control to be put into manual control at any time.

(g). After going over to manual, manual reset means must be provided to return the mechanism to automatic.

Summary The control starts with a speed sensing device which determines whether the speed selected manually for the centrifugal governor control of the normally operating pump is all right. If the manually selected speed is not attained somethingis wrong with the normal pump, the governor or the fuel passages connected thereto. Immediately a selector valve switches the control over tothe emergency pump subjected to the emergency manual control and to an emergency governor controlled by the speed sensing mechanism.

During acceleration obviously the speed is below' that selected by the manual control of the centrifugal overnor, hence, until acceleration is completed and governing has commenced the automatic switch-over must not be permitted to function prematurely.

The time delayafter acceleration has ended and'after governing has begun is adjusted by a leak orifice. Y E I I The manual control replaces centrifugal control and hence might wreck. the turbine at maximum demand, an override control to limit speed controlled by the speed sensing device is therefore provided- The pumps are provided with relief valves. Throttle valves are each provided with the usual constant pressure drop valves so that the flow at any throttle position does not depend on the efficiency of the fuel pumps. The

centrifugal governor is provided with the usual anti-droop device and overshoot preventative means, I

The figure is a diagrammatic illustration of the preferred form of my invention.

In the figure fuel enters the inlet passage 11 from a source maintained at approximately l5 pounds per square inch. A low pressure pump 9 with a pressure relief valve 1 directs fuel from the fuel tank 5 and furnishes fuel to the passages 'l'l. Two pressure pumps are provided which together with pump 9 are driven by the gas turbine 2l0. These pumps are:

(a) The primary pump ID, and (b) "The emergency pump I2.

These pumps are shown as the constant displacement type. The pressure in the passage [6 is thus maintained at approximately400 pounds per square inch. This fuel flows past a centrifugal governor valve 18 which is controlled by a centrifugal governor 20 driven from the gas turbine by a shaft H. Here the pressure drops to approximately 350-360 pounds per square inch. Relief valve 22 and spring 24 maintain this relationship which is a constant pressure drop at valve 18. Venturi 26, Pitot tube 28 maintain a pressure drop inchamber 30. This pressure drop is modified by restrictions 32 and 34. Passage 36 is connected directly to the Pitot tube 28.

A diaphragm 38 forms the left hand moving wall of chamber 40 also connected to the passage 36 through a restriction 42. A spring loaded check valve 44 also connects the chamber 4|] to passage 36 but only when the diaphragm 38 is moving to the right, that is, during deceleration.

Valve I8 is loaded by a spring 46 which is engaged on its right by the manually operated lever 48. A manually operated lever 5| and a cam 50 operated by this lever 5| engages with the upper end 54 of lever 48 and the lower end of shut-off valve 52. This upper end 54 is pivotally mounted on the upper end of lever 48 and is adjustable by means of the lowspeed adjustment 56. A compression spring 58 is interposed between diaphragm 38 and valve 88. All of the governor details are described in a copending application of Andrew William Orr, Jr., Serial No. 31,583 filed June '7, 1948.

An acceleration control valve I96 is responsive to airdensity and to a certain degree to air temperature in the air entrance to the gas turbine I62 and to the air compressor I64 leading to the combustion chamber I66 into which the fuel inlet manifold I24 discharges. This acceleration device is also described in said copending application, Serial No. 31,583. valve I'I9 moved by a partially evacuatedbellows I I2 enclosed in a chamber I14 and is provided with a circulation of air from the air entrance I62, through the Pitot tube I16 and restricted passage I18. This servomotor (pilot) valve I-IQ operates a slave piston R86 in a well known manner.

The response of this slave piston 586 to the servomotor (pilot) valve I16 is modified by the restrictions I82, I86 and 536. A piston I88 is subjected to the pressure in the upper part of chamber I99. The pressure in this chamber I90'm0dified' the action of'the partially evacuated bellows I72 as set forth in said copending application, Serial No. 31,583. The pressure in chamber I96 reacts against the small piston I88.

A spring loaded non-return valve I92 limits the pressure rise in the lower part of chamber I9I- and thus limits the pressure in the upper part.

High operating pressure for the slave piston I86 is admitted from the Pitot tube 28 through the pipe I94 when the valve I96 opens (as it does more and more as altitude increases endless-and less as temperature falls). The amount of fuel available during acceleration becomes less and less as altitude increases. Valve I96 returns fuel to the low pressure pipe system 11.

As fuel flows up passage I98, past shut-off valve 52, past non-return valve 206 where pressure drops 60 pounds per square inch, that is; to a pressure of between 280 and 300 pounds per square inch, the fuel flows past the emergency responsive valve 202, to the check valve 569, to the fuel inlet passage 29-4, past thespring loaded non-return valve 206, past the dump valve 268 to the fuel inlet manifold I24 from which the fuel discharges into the combustion chamber .166 and in burning provides the motive force for the turbine 2I9 which is also controlled by the movable tail piece 2I2. I c

The dump valve 208 is normally closed but when the turbine stops it rises under the influence of spring 2M and permits fuel remaining in the fuel inlet manifold I24 to escape overboard through the pipe 2I6. The pressure op-; posing the spring 2I4 is provided by the passage 205. Normally the pressure above valve 2|.4yis greater than the pressure, below valve 2l4 because of the pressure drop at valve 296. Hence, normally the dump valve 208 is closed andfuel freely-flows past the non-return valve 296' to the inlet manifold I24.

Emergency system The emergency pump I2 replaces the primary pump Ill whenever the speed selected by the lever is not reached by the turbine after accelera- It consists of a pilot passage 69. Ports 336 and 346 are connected with the high pressure fuel in chamber 69.

Springs 86 and 88 urge the piston towards the center and centrifugal force urges piston 99 down and Piston 42 up.

A'washer 350 is seated by the spring 88 and acts as the low speed stop to piston 99. Low

Speedspring 86 pushes the piston 99 up so that the port 344 admits low speed fuel to the chamber 35! at the lowest possible speeds.

A manually operated cam 68 engages a piston 22,2, and through piston 222 a piston 62 is also speed or fluid pressure responsive thereto.

orifice I06. Piston 228 then is held up until the reset mechanism is operated manually by opening the switch I04.

The reset mechanism 94 consists of an electricsolenoid which raises piston 249, compressing spring 242 which admits low pressure fuel from passage 11 to passage 244 which allows the spring 230 to reset the piston-valve 228 in the position in which it is shown. If it is desired to raise the piston valve 228 manually, the manually operated electric solenoid inside casing 250 is used to raise the piston-valve 228 independently of An electrical switch 102 controls the supply of electricity to the solenoid inside the casing .250. An electrical switch 164 controls the supply of electricity to the solenoid inside the casing 94.

Piston valve 228 acts as an intermediate servomotor valve to the selector valve 252 which is the slave of piston valve 228 in the following manner:

A passage 254 terminates in a port on the left controlled by servomotor valve 229, which is an extensionv of piston valve 228, as shown. Servomotor valve 229 closes the passage 254. Small perforations are provided in the piston which forms the upper end of selector valve 252. Passage 256 also terminates on the left in a port controlled by the end of servomotor valve 229, in the positionshown, and passage 256 is open to the low pressure fuel in the pipes 'I'I throughthe center of servomotor valve 229. There is a passage through the center of servomotor valve 229 communicating withthe chamber 260, above the piston 228. Chamber 260 communicates with the chamber 262 below the servomotor valve 228, through a restriction 264 in the passage 244. The piston forming the lower end of selector valve 252 is also perforated and'is provided with a spring-'255. Hence, the passage 266, which is the main escape-outlet from emergency pump I2, is shown returning to the inlet side 11 of the pipe system through a spring loaded non-return valve 268. This valve establishes 20 pounds per square inch pressure difference between the returnpassage 266 and the passage 11. This is the operating pressure for the servomotor valve 64. When in response to the rise of the servomotor valve 64 selector valve 252 rises and prevents the emergency fuel escaping down passage 266 and compels the emergency fuel pump to discharge down past the manuel control 4'I0.- When this happens thefuel from the-primary pump I0 T1 escapes through the passage 214, past the check valve 215, past the valve 252 and past the nonreturn valve 268.

The control has now passed over to the emergency system which consists of the manual valve 410, the emergency relief valve 412, and the constant pressure valve 414 which establishes an approximate 45 pounds per square inch drop across the manual valve 410. As there is no centrifugal governor 20 to protect the turbine 2I0, valve 216 is controlled bya diaphragm 218 and loaded by a compression spring 280. The chamber 286, to the right of diaphragm 218, is subject to the speed responsiv pressure in passage 99. This chamber 290, to the left of diaphragm 218, is subject to the fuel pump pressure in the passage 292 which is connected with high pressure chamber 69.

When the difference between the pressure in chambers 290 and 286 exceeds the pressure exerted by the compression spring 280 the valve 216 travels to the right lowering the pressure beneath the valve 414 because of the restriction 284. Valve 216 has a long taper and 280 is a long spring so that the turbine is held at a specific speed. 7

The fuel from the manual control 410 flows past an acceleration device which replaces the acceleration. device Il2-II4II0 etc., of the primary pump system.

The barometric element 288, in the chamber 294, is connected through the air passage 290 with. the air entrance I62 of the air compressor I64 of the gas turbine 2 I 0.

As before, a plunger 388 engages with a pilot valve 310 which controls a valve 380 which acts as a fiow divider. Fuel passage 492 flows down through and around valve 380 to passage 296, through and around constant pressure valv 298 and into the low pressure pipe system 11. ,Another portion of the fuel stream continues onvits way up through and around valve 380 to passage 300, past the shut-off valve 302, corresponding to valve 202. This valve 302 is loaded below with a compression spring 303 and also by the pressure from the primary pump I0, through the passage 304 so that when primary pump I0 is in action valve 302 is held firmly closed by the action of spring 303.

Fuel then flows through passage 204 and then through the non-return valve 206, past the dump valve 208 to the inlet manifold I24. A check valve 500 prevents fuel from passage 204 from flowing past the valve 202.

The control of the acceleration valv 380 is modified, as before, by the restriction 384 and 382 corresponding to the restriction I84 and I82. As before the pressure in chamber 390, acting on the plunger 388 slightly modifies the action of the evacuating or partially evacuated bellows 288.

Beneath the cam 68 is a piston 14 which engages with a diaphragm I43. Diaphragm I43 is the upper wall of a chamber I9. On the lower wall of this chamber is another diaphragm MI. The chamber I9 is connected with the pressure from the emergency pump system, that is with the pressure from the emergency pump I2, through a passage 502, through a resriction 504, through the spring loaded check 550 into the chamber I9. A compression spring I45 engages with a valve I44, which valve engages with the diaphragm I4I. A spring I40 keeps the diaphragm I43 in contact with the piston I4. A chamber 508 is connected to the chamber which in its turn is connected to the chamber 99. The chamber 508,.into which the valve I44 opens, is also connected to the chamber 05 and thus to the passage 99. When the valve I44 is open low pressure fuel from the passage 1! is admitted to chamber 508, that is to the chamber 95 through the restriction 5 I 0.

A time relay device is provided for a falling manifold pressure comprising a passage 204 connected to a chamber 5I2, to the left of the piston I54 which piston is pushed to the left by a spring I52. When th pressure in the passage 204 falls piston I54 travels to the left, pressure in chamber I55 falls and the normally closed valve I50 is opened by the travel to the left of the piston I5I. This lowers the pressure in the chamber I9 so that the spring I45 closes the valve I44.

After the acceleration ends and governing begins valve I50 opens immediately and the valve I44 closes so that the pressure in chambers 508 and 95 can build up and the normal functioning of the servomotor valve 64 can be resumed. By this means during acceleration the operation of the valve 68 will not interfere with the normal functioning of the device.

When the selector valve 252 descends into the position in which it is shown, pressure builds up in passage 214. This pressure is applied to Valve 225 which enables the pressure generated by the pump I2 to be applied to the upper side of valve 252 through the upper perforations in the valve 252. When the reverse happens and the valve 252 rises valve 225 moves to the right and con- 'nects the upper surfaces of valve 252 to the low pressure existing in the low pressure circuit 11.

When the shut off valve 52 is completely closed then the valve 400 opens in order to relieve all the internal pressure in passages I6, for example during the subsequent slowing down of the gas turbine.

A check valve 522 is provided to establish a small pressure difference (for example 3 to 4 pounds per square inch) between chamber I9 and chamber 506 (the pressure in chamber I9 being higher) up to the moment when cam 68 causes valve I44 to open.

A check valve 520 is provided to limit the decrease in pressure which occurs in chamber 508 when the valve I44 opens and low pressure is admitted from the low pressure pipe system 11 through restriction 5 I 0.

Operation I Assume that the cam 68 is rotated manually anti-clockwise rapidly and that the turbine accelerates. During acceleration the pressure in the fuel inlet manifold I24 and the pressure in passage 204 increases and the piston I54 travels to the. right and compresses the spring I52.

During this time the valve I50 is closed and the I fuel in the chamber I9, between the two diaphragms MI and I43, is for all practical purposes trapped as'the vent I4! is extremely small having an area of .0001 square inch. Hence, the diaphragms, MI and I43 both descend and the spring I45 is compressed and the valve I44 is opened as the shaft I6 descends. Low presmotor valve 64 is thus inoperative and remains inoperative until acceleration ends and governing begins. I50 immediately opens because thepressure in theinlet manifold I24 falls. Thevalve I50 is When governing begins the valve drawn to the left by the piston .II. for a short:

period of. time determined by theprifice I60. which permits the low pressure-fuel in -passage TI to enter chamber I55. The: pressure trapped,

created and thusthe valve I50 is opened so that valve I44 is closed and the normal. control. of the selector valve is resumed.

In theevent of the failure ofthe centrifugal governor in its closed position .or of the primar-y pump In so that necessary fuel is not provided during acceleration. the pressure in the pipe 204and chamber 5I2 falls, piston I54moves,

to the left and sucks piston I5I' to the left which opens the bleed valve I50 and closes valve I44 and thus re-establishes speed sensitive pressure in-chamber 95. This action throws servomotor valve 6411p and move valve 228 up which moves selector-valve 252 up. This puts thedevice in the position for manual operation.

When this happens servomotor valve 64 ascends and pressure is applied below the valve 228and the moment valve 228 rises hydraulic pressure through restriction 100 enters the chamber 262 and positively holds the piston 223 u even if the valve 64 descends so that no hunting can take place.

In the operation of the valve I44 the effective size of valve I44 has to be reduced and for this reason a restriction is provided, the area of 5I0 being comparable to the area of the seat of the valve I50.-

With piston 228 in its up position the passage 254,- above selector valve 252, is put into communication with low pressure passage I! so that valve 252 rises under the influence of spring 255. At the same time passage 2561s put out of communication with the low pressure circuit TI. High pressure immediately builds up in passage 256 through the lower perforations in the valve 252. The rise of valve 252 blocks the escape of the fuel from pump I2, down pipe 266. Hence, fuel flows above 492, past flow divider 380, along pipe 300, past valve 302 which opens when pressure in pipe 304 falls. The pressure in pipe 304 falls because pipe 304 is connected to'passage 254 which is now connected to the low pressure circuit 7 I.

To reset the device-The switch 1041s closed and valve 240 rises. Low pressure is then'applied through passage 244 to below piston 228. Spring 239 then pushes piston 228 down back intothe position in which it isshown. The pressure above and below the selector valve 252 is now reversed and the valve 252 returns to the position in which it is shown.

Override manual controZ.-'If it is desired to place the device in its manual position for any reason the switch I02 is closed, the piston 228 is raised by the electric magnet inside casing 250 and the hydraulic pressure above and below selector valve 252 is once more reversedand again the pump I0 is rendered inactive and the pump I 2 is put into action.

Governor 70."In the upper left hand corner a centrifugal governordriven' by shaft-10:-is:

shownwhich has this efiect onthesystem when in its emergency condition: Assumethat the manual control 'valve 410 is in active control of the gas turbine becausethe speed selected by cam 58-Was not reached in a reasonably short period oftime: as. already related. Then assume that aniexcessive speed is attained, at any rate a:- speed close to the limiting (dangerous) speed;

In that event :the pressure difference on dia-.,- phragm2l8 becomes greater than the pressure exerted by the spring 280. The tapered .valve 276' moves to the right, The, pressure belowthe valve 414 falls and the fuel flow "fromthe man-.-

.ual valve 410, along;passages 492;-300 into pas-x Hence, this centrifugal gov.-.-

sage 204 "drops. ernor not only. actsduring the automatic operaticn as a speed sensing device .to: see to'it that" the speed selected by the variable .speed governor '20 is attained butafter the primary pump I 0 has...

failed the governor I05062, etc., remains act-J ing as a speed limiting device,

In the event that the governor 20"sticks,.

that is, fails irritsclosed position they failure 'of the pump I0, the effect of which has .just been described, would be duplicated.

In the event that the governor .20. failed inits wide open position thenthe governor driven by. r shaft is would immediately take over .thecon trol as follows: Centrifugal force of weight 30." would overcome spring 88 at a speed slightly above normal maximum. This would open up;

port 346 and admit high pressure fromchamben 63, through pipe 99 and to chamber 220. Spring 91 thereupon pushes up piston .62 and servovalve '64. This valve 64 admits high pressurefrom chamber 224. to the passage 226andthus Piston .228 rises and causes to chamber 262. piston 252 to rise.

What -I claim is: 1..In.a manually controlled normally operatinggovernor control for a gas turbine combined with an emergency control system, the combinationincluding first and second turbine'driven fuel pumps, a normaloperating governor .con-- trolledfuel supply valve for the first pump and an emergency manually" controlled fuel sup--- ply valve for the second pump, an automatically operated selector valve to substitutethe manually controlled emergency fuel supply for the governor. controlled normal fuel'supply wheneverthe governor controlled valve fails to furnish sufiicient fuel to permit the turbine to attain the speed for which the governor" is manually set, meansto prevent the premature shift from automatic to manual comprising a manually op-- erated cam interconnected with the manual con-'= trol of said governor, a springcontrolled by said" cam, a speed sensitive hydraulic device driven by said turbine which controls a variable hydraulic pressure indicative of speed, a moving wall the movement of which is responsive to said variable hydraulic pressure and to the variable spring pressure acting in opposition to- :eachother, a servomotor valve connected to said mov-'= ing wall and controlling said selector valve when even the variable hydraulic pressure corresponds 1- to a speed-below'the selected speed, a chamber connected to the normal fuel supply downstream of the manually controlled governor valve, a moving wall in said chamber subject to the pres"- sure therein, a chamberon the opposite sideof;

said moving, wall connected to the low pressure side of saidfuel supply systemya first bleed valve 0 adapted tobe opened by the movement of said moving wall in response to a sudden drop in pressure in said chamber due to the action of said governor valve, said first bleed valve acting as a bleed to a chamberhaving a moving wall and connected to the high pressure side of said fuel system, the other side of said moving wall being responsive to the speed sensitive pressure, a second bleed valve also communicating with the low pressure fuel system and connected to the last mentioned moving wall, a third moving wall also connected to said cam, yieldable means opposing its movement, said third moving wall forming another wall of said last mentioned chamber so that the pressure therein rises whenever any increase in speed is calledfor by the movement of the cam and the movement of the manual control of said governor, the second bleed valve being adapted to open as a result of this movement of said third moving wall, whereby said second bleed valve lowers the speed sensitive pressure during acceleration to prevent the premature operation of the selector valve, the first bleed valve causing the second bleed valve to close at the end of acceleration so that the normal control of the selector valve is resumed.

2. In aomanually controlled normally operating governor control for a gas turbine combined with an emergency control system, the combination including a normally operating governor controlled fuel supply valve and an emergency manually controlled fuel supply valve, an automatically operated selector valve and control means therefor to substitute the manually con trolled fuel supply for the governor controlled fuel supply whenever the governor controlled valve fails to furnish suificient fuel to permit the turbine to attain the speed for which the gov ernor is manually set, said selector valve and control means therefor comprising a spring loaded servomotor valve, a third manually controlled means for varying the spring load on said valve, a speed sensitive hydraulic device driven by said turbine which controls a variable hydraulic pressure indicative of speed, means whereby the spring load on said servomotor valve is balanced against said variable hydraulic pressure, a spring loaded slave valve, passages connecting said slave valve to said servomotor valve, passages connecting said slave valve to said selector valve where- 50 by said slave valve acts as a servomotor valve to said selector valve, hydraulic means for holding said slave valve in the position into which it is moved when it moves the selector valve into the position in which the governor controlled valve is rendered inoperative and in which the manually controlled valve becomes operative,

means for operating said third manual control means simultaneously with the first manual control which controls the normally operating governor and with the second manual control which controls the emergency fuel supply? 3. A device as set forth in claim 2 in which there is an electric magnetic control means for moving said slave valve independently of said servomotor valve including an electric circuit and a manually operated switch therefor.

A device as set forth in claim 2 in which there are means to reset the device from the manual position to governor controlled position comprising an electromagnet, an electric circuit therefor, a manually operated switch therefor, .a valve operated by said electro-magnetic means, a passage in the low pressure fuel circuit controlled by said valve and leading to said slave valve to neutralize the effect of said servomotor valve so that the slave valve moves back into its original position under the influence of the spring which imposes a load on it.

5. A gas turbine fuel control device which includes a source of fuel under a relatively low pressure, two turbine driven fuel pumps, one for normal operation the other for use in an emergency, a double acting selector valve for switching from normal to emergency operation comprising two cylindrical piston valves having crowns which are connected together by a piston rod, two end cylinders in which the two pistons slide, an intermediate cylindrical chamber between the two pistons located around said rod, an escape outlet from said chamber, two escape passages leading one from each of said pumps and surrounding each of said piston valve so that when one passage is blocked by one of the piston valves the other passage is open, the pressure in the cylinder of the piston valve blocking the emergency pump outlet being normally connected to the low pressure side of the fuel system so that the pressure of the fuel escaping from the emergency fuel pump acts to hold the selector valve in this its normal position, means responsive to the failure of the normal fuel supply means to reverse the fuel pressures acting on said pistons of said selector valve so that the selector valve moves into its emergency position and the outlet from the emergency fuel pump is now blocked and the outlet from the normal fuel pump is now open to the escape outlet from said cylindrical chamber.

6. A device as set forth in claim 5 in which the means for reversing the pressure acting on the ends of said pistons of said selector valve comprise a restricted passage between each end cylinder and the intermediate cylinder, speed responsive means for moving said valve when the speed falls below a preselected value, a spring loaded slave valve, a passage controlled by said servomotor valve to apply fuel under pressure to said slave valve to move it against the action of the said spring when the speed falls below said preselected value, two passages each one connected so as to release the pressure from each end cylinder of said selector valve, said pressure being derived from the restricted passages from said end cylinders, valve means connected to said slave valve to release the pressure in one of said passages when the slave valve is in one position and to release the pressure in the other passage when the slave valve has been moved into its other position so as to reverse the pressure acting on the two ends of said selector valve.

7. A device as set forth in claim 5 in which the means for reversing the pressuresacting on the ends of said pistons of said selector valve comprise a restricted passage between each end cylinder and the intermediate cylinder, a servomotor valve, speed responsive means for moving said valve when the speed falls below a preselected value, a spring loaded slave valve held in its normal position by said spring, a passage controlled by said servomotor valve adapted to supply pressure to move said slave valve against the action of said spring when the speed falls below said preselected value, another passage normally blocked by said slave valve and connected to fuel under pressure and adapted when said slave valve is moved by said servomotor valve to apply said pressure to said slave valve to prevent the spring restoring the slave valve to its original position v should the servomotorvalve move back into its original position; two passages each one conl 1 nected was to release the pressure from-each end of said selector-valve'said pressure being derived from the restricted passagesfrom-said end cylinders, valve means connected to said-slave valve to release the pressure in one -of said passages when the-slave valve is in one position and to release'the pressure in the other passage when the slave valve'has been moved into itsiother position was to reverse the pressures acting on the two ends-of saidselector valve.

8.- A device as set forth in claim 5 in which the means for reversing the pressures acting on the ends of said pistons of-said selector valve cornprise a restricted passage'between each end cylinder and-the intermediate cylinder, a servomotor 1 valve, speed responsive means for moving said valve when the speed falls below a preselected value, a spring loaded slave valve held in its normal position by said spring, a passage controlled by said servomotor valve adapted to supply pressure to move said slave valve against the action of said spring when the speed falls below said preselected value, another passage normally blocked by said slave valve and connected to fuel under'pressure andadapted when said slave valve is moved by said servomotor valve to apply" said pressure to said slave valve to prevent the spring restoring the slave valve to its original position should the servomotor valve'move back into its original position, two passages each :one connectedso as to release the pressure from .each end of said selector valve, said pressure being derived from the restricted passages from said end cylinders, valve means connectedto said slave valve to release the pressure in one of said passages when the slave valve is in one position and to release the pressure in the other passage when the slave valve has been moved into its other position so as to' reverse the pressures acting on-the two ends of said selector valve, and manual means for moving said slave valve into its emergency position and positivelyholding it in that position.v

9. A device as set forth in claim 5 in which the means for reversing the pressuresacting on the ends of said pistons of said selector valve comprise a restricted passage between each end cylinder and the intermediate cylinder,,a servomotor valve, speed responsive means for moving said valve when the speed falls below a preselected value, a spring loaded slave valve held in itsinormal positionby said spring, a passage controlled by said servomotor valve adapted to supply pressure to move said. slave-valve against the action of saidspring when the speedialls .below said preselected value, another passage. normally blocked by said slave valve and connected to fuel under pressure and adapted when said slave valve is moved by said servomotor valve to apply said pressure to said slave valve to prevent the spring restoring the slave valve to its original position should theservomotor valve move back into its original position, two passages each one connected so asto release the pressure from each end of said selector valvasaid pressure being derived from the restricted passages from'said end cylinders, valve means connected to' said slave valve to release the pressure in one of said passages when the. slave valve is in'one position and to release the pressure in the other passage when the slave valve hasbeen moved into its other position so as to reverse the pressures acting on the two ends oiisaid selector valve, and manual means for resetting the slave valve in its normalzpositionqafterithas been moved into its emergency position.

10:. A device asset forth in claim 5 in which the means for reversing the pressures actingon the ,ends of said pistons of said selector valve comprise a restricted passage between each end cylinder and the intermediate cylinder, a'servomotor valve, speed responsive means for moving said valve'when the speed falls below a preselected .value, a spring loaded slave valve held in its normal position by said spring, a passage controlled by said'servomotor valve adapted to supply pressure to move said slave valve against the action of said spring when the speed falls below said preselected value, another passage normally blocked by said slave valve and connected tofuel under pressure and adapted when said slave valve .is moved by said servomotor. valve to apply said pressure to said slave valve to prevent the spring restoring the slave valve to its original position should the servomotor valve move back into its original position, two passages each one connected so as to release the pressure from each end of said selector valve, said pressure being derived from-the restricted passages from said end cylinders, valve means connected to said slave valve torelease the pressure inone of said passages when the slave valve is in one position and to release the pressure in the other passage when the slave valve has been moved into its other position so as to reverse the pressures acting on the two ends of said selector valve, manual means for moving saidslave valve into its emergency position and positively holding it in the position, and manual means for resetting the slave valve in its normal position after it has been-moved into its emergency position;

113A device asset forth in-claim 5 in which the means for reversing the pressure acting on the ends of said pistons of said selector valve comprise a restricted passage between each end cylinder and the intermediate. cylinder, speed responsive means for moving said valve when-the speed falls below a preselected value, a spring loaded slave valve, a passage controlled by said servomotor valve to apply 'fuel under pressure to: said slave valve to move it'against the action of the said spring whenthe' speed falls below said preselected value, two passages each ,one connected so as to release the pressure from each :end cylinder of said selector valve, said pressure being derived from-the restricted passage from saidend cylinders, valve means connected to said'slave valve to release the pressure in one of said passages when the slave valve is in one position and to release the pressure; in the other passage when the slave valve has been moved into its other position so as to reverse the pressure acting-on the two ends-of said selector valve, and manual means for moving said slave valve into its emergency position and positively holding itin that position.

12-. A device as set forth in.-claim'l in which there is a spring engaging with the moving wall located in the chamber connected to the fuel pressure downstream of the governor valve, so that the chamber expands during the acceleration periodwhich follows the movement of themanually operated governor control in the direction calling for an increase in speed and which chamber decreases in volume when the acceleration period is completed and the governor valve acts to cause the pressure in said chamber to fall.

LEONARD W. KEIL.

No references cited; 

